JP6111279B2 - Reclining mechanism for vehicle seat - Google Patents

Description

(Cross-reference of related applications)
This international patent application claims the benefit of US Provisional Patent Application No. 61 / 233,321, filed Aug. 12, 2009, entitled “Continuously Engaging Recliner Free System and Precision Stamped Gear Hub”. . The entire disclosure of the above application is considered part of the disclosure of the present application and is incorporated herein by reference.

  The present invention relates to an adjustment device for a vehicle seat, and more particularly to an inclination adjustment device that enables a seat back of a vehicle seat to move relative to a base of the vehicle seat.

  This tilting device, also referred to as a reclining mechanism, generally includes an internal gear and an external gear that are movable relative to each other to provide relative tilt adjustment of the seat back relative to the seat base. Generally, the internal gear is fitted within the external gear and is at least one tooth smaller so that the rotation adjustment element drives the eccentric ring or carrier about the axis and the wedge segment is dragged to be eccentric about the axis of rotation. When pushed in, the external gear moves radially about the axis. Generally, for one revolution of the carrier and wedge segment, the external gear is moved approximately 10 degrees around the axis. When the seat back is in the preferred position, the relative movement of the internal and external gears is locked by a wedge segment that ensures that the internal and external gears remain engaged.

  The rotation mechanism is generally called a five-door rotation reclining mechanism. The 5-door reclining mechanism is suitable for a vehicle seat having a single door behind the seat of the seat provided with the reclining mechanism. For example, reclining mechanisms for five doors are often found on the front seats of sedans, SUVs, and minivans. However, for some seat positions such as the coupe front seat, station wagon, SUV, minivan center seat, 5-door or rear seat of a hatchback car, it is sometimes desirable to allow the seat back to freely pivot forward. For example, it may be desirable to fold the seat back to allow quick access without using a five-door rotary reclining mechanism. In general, a reclining mechanism including these additional functions that allows the seat back to freely move with respect to the seat base under a certain condition is called a three-door rotary reclining mechanism. A three-door reclining mechanism generally includes the five-door mechanism modified with minor changes and an additional latch assembly that engages the gear teeth at the outer end of the outer gear. Generally, the latch assembly is released from engagement with the external gear of the five-door reclining mechanism so that the seat back can rotate independently of the five-door reclining mechanism included in the three-door reclining mechanism. Enable. In some embodiments, the free rotation of the vehicle seat back also allows the additional element to release the track so that it can easily enter and exit from the vehicle seat, allowing the seat to slide forward in one motion. to enable.

  The external gear and internal gear of the reclining mechanism for five doors, and similarly, the external gear and the internal gear of the reclining mechanism for five doors when used with an external gear modified in combination with the latch assembly of the rotary reclining mechanism for three doors Generally, it is stamped from mild steel so that gears can be easily formed. Mild steel allows metals to be easily formed without becoming brittle or cracking during various forming processes. In particular, the external gear includes a hub that extends outwardly from the original surface of the sheet of metal, which has forced manufacturers to use only mild steel for the formation of external gears for a long time. In order to use mild steel for the forming process of the internal and external gears, the manufacturer had to heat treat the gear when the forming process was completed. The heat treatment process hardened the gear, thereby increasing the average life and improving wear resistance. Heat treatment is time consuming and expensive, adding additional processing steps. The reason why most internal gears and all external gears are formed from mild steel such as 1020 steel, 4130 steel, or 4140 steel is because the high carbon content of high strength steels makes them brittle and the forming process, especially the outer During the formation of the hub extending to the center, the end of the hub is cracked or broken in contact with the external gear. Therefore, manufacturers realized that it was impossible to punch external gears from high quality steel while eliminating the heat treatment process.

  The rotary reclining mechanism further includes a carrier that presses the pair of wedges against the bearing inside the internal gear. The carrier is rotated to press the internal gear against the external gear. The internal gear is configured to have one or more fewer teeth than the external gear so that when the internal gear is forced to engage the external gear and the carrier rotates for each revolution of the carrier, the external gear Pushed approximately 10 degrees around the axis of rotation. Certain designs of the carrier allowed unintentional swinging of the seat back because the main pressure point on the bearing was centered between the two wedges while providing sufficient wedge functionality. Further, in the seat assembly in which the power tilt mechanism is frequently used, the design of the carrier and the bearing may cause an early failure.

  Thus, to date, manufacturers have been unable to provide a rock-resistant carrier with improved lifetime.

  The present invention relates to a seat adjusting device, and more particularly to a seat back tilt adjusting device. The adjustment device includes an internal gear and an external gear that are movable relative to each other to provide relative adjustment of the seat back relative to the seat frame. After a suitable adjustment of the seat back has taken place, the internal and external gears are locked from such relative movement by the use of eccentric elements driven by the adjusting elements.

  The present invention uses an external gear forming process that forges and forms the external gear. This forging process creates a concave surface at some point to transfer material from the end cap of the hub that is later discarded to the hub itself. By forming a concave surface in a specific region described in the detailed description below, the present invention can use harder steel than before and eliminate the need for an additional heat treatment step. Also, the forging and forming process further temper the material further so that when the external gear is finally formed, the hardness of the material that eventually occurs in the wear area adjacent to the forged portion increases.

  The present invention utilizes a carrier having at least three excellent features in order to create a rock-resistant and long-life carrier. The carrier of the present invention also utilizes a carrier tab centered between the wedges that press against the bearing surface to provide an additional load surface. Further, the inner peripheral surface of the carrier is contoured so as to be substantially non-circular. More specifically, the carrier is shaped to have a contoured portion under the carrier tab, so that the center hub of the external gear just below the carrier is not loaded. Instead, the load on the hub of the external gear is displaced on both sides of the carrier tab and occurs under the wedge. Thus, the two points of displaced contact prevent the seat back from swinging as the load is applied directly under the carrier tab or with the carrier in the center between the two wedges. The first contoured surface of the inner peripheral surface also accepts pockets where additional grease can accumulate, thereby providing increased life. To further provide anti-swing behavior and further extend life, the carrier also includes a second contoured portion, in some embodiments, directly opposite the first contoured portion.

It is a partial exploded perspective view of a rotation reclining mechanism. It is a perspective view of a rotation adjustment element. FIG. 3 is a cutaway side view of a rotation adjustment element bearing, carrier, and wedge. FIG. 3 is a perspective view of a carrier and wedge incorporated within a bearing and rotation adjustment element. FIG. 5 is an assembled side view of the carrier and wedge incorporated within the bearing and rotation adjustment element. FIG. 5 is an assembled side view of the carrier and wedge incorporated within the bearing and rotation adjustment element. FIG. 3 is a perspective view of a carrier and wedge incorporated within a bearing and rotation adjustment element. FIG. 4 is an enlarged side view of a carrier and wedge incorporated in a bearing and rotation adjustment element showing the contoured portion and the displaced load point. It is a perspective view of the inner surface of the external gear which shows the shape | molded center hub. FIG. 5 shows a rear perspective view of an external gear cut in half to better illustrate the contours of various portions of the external gear. FIG. 4 illustrates a first step of forming a metal sheet to have a sealed hub with a concave end cap. 12 shows the opposite side of the metal sheet of FIG. FIG. 13 shows a cross-sectional view of a die used to form the metal sheet of FIGS. 11 and 12, and the metal sheet is shown in cross-section between the dies after forming. Fig. 4 schematically illustrates removal of an end cap from a hub. FIG. 5 is a perspective view of a partially molded inner surface of a gear that surrounds a hub. It is a perspective view of the outer surface of the external gear of FIG. FIG. 17 is a schematic view of a die used to form a metal sheet as shown in FIGS. 15 and 16, including a cross-sectional view of the metal sheet between the dies after forming. Fig. 5 shows the inner surface of the external gear after an additional molding step on the outer end of the hub. FIG. 19 is a perspective view of the outer surface of the external gear of FIG. 18 showing an additional molding step on the hub. FIG. 20 is a schematic view of a cross-section of a die used to form the metal sheet of FIGS. 18 and 19 and a cross-sectional view of the metal sheet after molding in between. It is a perspective view of the outer surface of the completed external gear. It is a perspective view of the inner surface of the completed external gear of FIG. FIG. 23 is a schematic view of a cross section of a die used to form the external gear shown in FIGS. 21 and 22, with the external gear after forming shown in cross section between them.

  The present invention is generally directed to a rotational reclining mechanism or adjustment device 10 that is generally used to provide a motorized tilt adjustment for a seat base seat back about a rotational axis 14. Is done. The rotary reclining mechanism 10 can exist in various configurations, and can be generally applied to what is usually called a five-door rotary reclining mechanism or a three-door rotary reclining mechanism. It should be understood that the modified five-door rotary reclining mechanism is generally included in the three-door rotary reclining mechanism, particularly by fine adjustment to the external gear 30. For example, an external gear generally has an outer end with a different profile depending on whether the external gear is configured in a five-door rotary reclining mechanism or in a three-door rotary reclining mechanism. Are known. Although not shown, the external gear is generally configured to have gear teeth that engage the latch mechanism to allow free tilt about the seatback rotation axis in the three-door rotary reclining mechanism. . As shown in FIG. 1, the main components of the rotary reclining mechanism 10 are a washer or retainer 20, an external gear 30, an internal gear 70, a bearing 90, a wedge 102 and an eccentric ring or carrier 120. The assembly 100 includes a spring 170 and a rotation adjustment element 180. When assembled, they together form a rotating reclining mechanism 10. The washer or retainer 20 is generally configured to fit around the hub 184 of the rotational adjustment element 180, thereby connecting all the elements in FIG. 1 above.

  The external gear 30 can have a variety of styles, shapes, and configurations, depending on the desired embodiment in which it is placed, but the external gear 30 generally includes an outer portion 32 having an outer end 34 and a toothed portion. An intermediate portion 40 including a region 42 and an inner portion 50 having a center hub 56 are included. The external gear 30 shown in the figure is generally used in what is commonly known as a five-door rotary reclining mechanism. However, the external gear can be easily used in other rotary reclining mechanisms to which the present invention can be applied by other minor changes to the contour.

  The external gear 30 may generally include a first side surface 26 and a second side surface 28. The first side surface 26 can also be referred to as the inner surface of the external gear, and the second side surface 28 can also be referred to as the outer surface of the external gear. The outer portion 32 generally includes an extension 33 having an outer end 34. Outer end 34 and extension 33 may be configured as desired to suit a variety of different applications. The outer portion 32 may also be considered to have a first surface 36 and a second surface 38 that generally form a plane.

  The intermediate portion 40 generally includes a tooth region 42. The tooth region 42 generally includes female gear teeth 44 on the inner surface 26 and male gear teeth 46 on the outer surface 28. The female gear teeth 44 and the male gear teeth 46 are the result of stamping the gear teeth on the external gear 30 so that the external gear 30 is molded and defined by the intermediate portion 40 and the inner portion 50. If 48 has female gear teeth, the internal gear 70 can be disposed therein.

  The inner portion 50 can have a variety of styles, shapes, and configurations depending on the desired application of the external gear 30. Inner portion 50 may be configured to be welded to other members including a raised portion, which may be configured to provide other gears as desired for operation with rotary reclining system 10. Acts as a welding surface for the forming technique. In the case of the illustrated external gear 30, the inner portion generally includes a first portion 52 that extends inward toward the center of rotation or axis 14 and an optional second portion 54 that is recessed from the first portion 52. The inner portion 50 includes a center hub 56 that extends from the plane formed by the first portion 52 into the gear cavity 48 and in some embodiments beyond the first surface 36 of the inner surface of the external gear. Extends outward. The center hub 56 extends a predetermined distance into or beyond the gear cavity 48 and is generally configured to have an outer peripheral surface 58 and an inner peripheral surface 60. The inner peripheral surface 60 generally defines an axial opening having a specific diameter within the center hub 56 and terminates at an end surface 64. As shown in the figure, the end surface 64 can be formed to have various inclined surfaces. As shown in FIGS. 11 and 12, during the molding process, the center hub 56 may include an end cap that is later removed, and during the molding process, the end cap may have a concave surface 69. Also, the outer surface 28 of the external gear 30 can be configured to have various bevels or other shapes as desired around the area of the center hub 56. Although not shown, the concave surface 69 may also be inside the end cap 68, or both sides of the end cap 68 may include concave surfaces.

  The internal gear 70 generally includes an outer portion 72, a gear portion 78 having male gear teeth 80, and an axial hub 82 having an inner ring 84. The internal gear 70 generally fits within a gear cavity 48 formed by the external gear 30. The male gear teeth 80 generally have one, fewer, or even two or more fewer gear teeth than the female gear teeth 44 of the external gear 30. The axial hub 82 formed by the internal gear 70 includes an inner ring 84, and the bearing 90 is disposed in contact with the inner ring 84. In some embodiments, the bearing 90 may be free to rotate in contact with the inner ring or may be configured to rotate freely; in other embodiments, the bearing 90 may be configured relative to the inner ring 84. Can be press-fitted.

  The bearing 90 generally includes an inner surface and an outer surface 94, and the outer surface 94 is configured to engage the inner ring 84. The bearing 90 also generally has a width that is equivalent to the axial hub 82 of the internal gear 70. The bearing 90 is generally formed as is well known in the art.

  The eccentric element assembly 100 is configured to fit within the bearing 90, specifically the inner surface 92 where it rotates in contact with the inner surface 92 and applies pressure to one region of the bearing 90. The eccentric element assembly 100 is generally formed from an eccentric ring or carrier 120 and a wedge 102 disposed between the carrier 120 and the inner surface 92 of the bearing 90. The wedge 102 is generally configured to have an outer surface 104 that presses against the inner surface 92 of the bearing and an inner surface 106 that presses against the carrier 120. The wedge 102 has a wide end 108 and a narrow end 110 that is configured to be proximate to a carrier tab 132 on the carrier 120. The wedge 102 may also further include a notch 112 at the wide end 108.

  The carrier 120 generally includes a circumferential portion 122. The circumferential portion 122 has an inner surface 124 and an outer peripheral surface 126 interrupted by outwardly extending carrier tabs 132. The outer peripheral surface 126 includes a region of the wedge load surface 128 proximate to the carrier tab 132. One or more drive tabs 130 may extend from the circumferential portion 122 approximately parallel to the rotational axis 14 that also generally serves as the center of the radius of the circumferential portion 122. The carrier tab 132 may be molded in a variety of sizes, shapes, and configurations, but generally includes a carrier tab loading surface 134 that is in close proximity to the inner surface 92 of the bearing 90. Extending between the carrier tab load surface 134 and the circumferential portion 122, particularly the outer peripheral surface 126, is a carrier tab side surface 136. The carrier tab 132, particularly the carrier tab load surface 134, is configured to support the inner surface 92 of the bearing 90 when a high load, such as a collision load, is seen on the reclining chair. This load tends to collapse the central region and the carrier tab 312 resists this collapse. More particularly, the carrier tab 132 acts as a brace between the bearing 90 and the hub 56 in high load situations to distribute the load and increase load bearing capacity to make the recliner stronger. Can do. The applied load is an eccentric load. As a result, when the carrier tab rotates inside the bearing 90, the male gear teeth 80 of the internal gear and the female gear teeth 44 of the external gear 30 that are approximately radially aligned with the carrier tab 132 are directly engaged. This radial alignment extends from the rotating shaft 14 through the carrier tab 132. In contrast, the directly opposed male gear teeth 80 and female gear teeth 44 are disengaged as described above because the internal gear 70 has one fewer gear teeth than the external gear 30. The Therefore, when the carrier 120 rotates in the bearing 90, the internal gear comes in eccentric contact with the external gear by the eccentric load applied through the carrier tab 132 and the wedge 102. As a result, since the internal gear is driven to engage with the external gear in this eccentric manner, the external gear is forcibly rotated with respect to the internal gear. More specifically, as described above, the external gear is driven approximately 10 degrees in the radial direction around the rotation axis with respect to one rotation around the rotation axis 14 of the carrier 120.

  In order to improve the life of the carrier 120 and the life of the rotary reclining mechanism 10 and to provide an anti-swing configuration, the carrier 120, particularly the inner surface 124, includes at least one inner contoured portion 140. The addition of these inner contoured portions 140 is not a perfect circle in which the inner surface 124 of the carrier 120 has a constant radius from the axis of rotation 14, and instead, the inner contoured portion 140 is not considered an inner contoured portion 140. It means that the distance from the rotation axis 14 to the inner surface 124 is slightly larger than the area. In the illustrated embodiment, the inner contoured portion includes a first contoured region 150 and an optional second contoured region 160, particularly as shown in FIG. The first contoured region 150 occurs directly below the carrier tab 132 on the inner surface 124 and creates the anti-sway function of the rotary reclining mechanism 10 of the present invention. The first contoured region 150 generally extends completely under the carrier tab 132 and generally extends a distance toward the bottom of the wedge 102 on both sides of the carrier tab 132. The place where the first contouring region ends and the inner surface 124 returns to a predetermined radius is the displaced inner load region 154. The displaced inner load region 154 is spaced apart on either side of the carrier tab 132 under the wedge 102. By displacing the load area 154 from directly below the carrier tab 132, which is generally common, instead of a single point load that can cause the external gear to swing, the two displaced load areas have a stable anti-vibration configuration. I will provide a.

  The second contoured region 160 is generally on the opposite side of the inner surface 124 from the first contoured region 150. The second contoured area 160 is optional but shown in FIG. 8 and allows an additional grease pocket for grease to be placed so that when it rotates within the bearing 90, The life of the carrier 120 is improved.

  The rotational reclining mechanism 10 may further include a plurality or one spring 170 having a radial portion 172 and a leg end 174. The spring 170 is generally configured to place the wedge 102 in an appropriate position between the carrier 120 and the bearing 90 and hold the wedge 102.

  The carrier 120 is driven into rotational movement by a rotation adjustment element 180. The rotation adjustment element 180 generally includes an outer cover 182, a hub 184 extending from the outer cover 182, and a female shoulder 194. The female tooth shoulder 194 engages with the drive tab 130 of the carrier 120 and, when the rotation adjustment element rotates, the female tooth shoulder 194 engages with the drive tab 130 and causes the carrier 120 to rotate within the bearing 90. The hub 184 of the rotation adjustment element 180 may further include a retainer ring groove 188 with which the retainer or washer 20 is coupled together to assemble a complete mechanism. The rotation adjustment element 180 may also include a track support 190 having a track surface 192. The track support 190 prevents the wedge 102 from being displaced from the wedge load surface area 128 on the carrier 120. The hub 184 can include an axial hole 186 having a key stop with which a power drive mechanism is engaged to rotate the rotation adjustment element 180.

  As described above, the present invention provides a unique method of forming the external gear 30. Conventionally, the external gear 30 has been formed from mild steel such as 4130 steel or other low carbon steel, and has been heat treated to increase its strength. Some manufacturers have attempted to make external gears from high strength steels such as 550X steel, 550XF steel, or S700 steel with higher carbon content, but the problem is the considerable amount required for external gear 30 It was easy to crack in various places of the external gear for molding. Thus, at the present time, manufacturers have not been able to mold external gears from high carbon content steels such as 550X steel.

  The present invention begins with a flat sheet of high carbon content steel, such as 550X steel, and subsequently processes the steel by both forging and forming processes. As shown in FIG. 11, first, the center hub 56 including the end cap 68 is formed. As further shown in FIG. 13, when the hub 56 is molded, the die 200 uses the convex die 202 to create the concave surface 69 shown in FIG. Thus, when the hub 56 is molded, the die 200, specifically the convex die 202, strikes the center hub 56 with an end cap having a concave surface 69 and the end face 64 of the center hub 56 from the center of the end cap 56. Move material to. This movement of material compresses the end cap 68 and causes the material to flow outside the center hub 56, particularly near the end face 64, thereby preventing cracking during molding of the hub 56. 11, 12 and 13 show only the formation of one concave surface 69, but on the inner side 26 of the external gear 30, the opposite side of the end cap 68 or both sides of the end cap 68 may include the concave surface 69.

  After the center hub 56 is partially molded with an end cap 68 having a concave surface 69 as shown in FIG. 14, the end cap 68 can be stamped from the metal sheet forming the external gear 30. Of course, there may be other molding processes during the stamping process, such as the shape molded in FIGS. Although the process after forming the concave surface 69 and the end cap 68 on the center hub 56 may vary, the present invention generally shapes the contour of the inner portion 50 of the external gear 30 in the exemplary process. The contours of the inner portion 50 shown in FIGS. 15 and 16 are exemplary and may vary depending on the desired configuration.

  After the inner portion 50 of the external gear 30 has been molded to the desired profile, the present invention cold forges the center hub 56, and more particularly creates a particular ramp as clearly seen in FIGS. These inclined surfaces are chamfered surfaces, resulting in further cold forging of the center hub, creating a harder surface that does not require heat treatment. FIG. 20 generally shows an exemplary set of dies 200 used to perform the molding of the inner contoured portion 50 and the additional molding process to the center hub 56.

  FIGS. 21 and 22 further illustrate the shaping of the outer portion 32 and the intermediate portion 40, particularly the tooth region 42. The die 200 generally supports the molded center hub and half-pierces the intermediate portion 40 of the metal sheet to form a tooth region 42 having female gear teeth 44 and male gear teeth 46. The die 200 can continue to approach the outer gear 30 from the metal sheet to form the outer end 34 and the extended portion 33. The completed gear is shown in FIGS. 21 and 22, and an exemplary die 200 used for molding is shown in FIG.

  The foregoing invention has been described in accordance with the relevant legal standards, and thus the description is exemplary rather than limiting. Changes and modifications to the disclosed embodiments will be apparent to those skilled in the art and are within the scope of the invention.

Claims (10)

A reclining mechanism for a vehicle seat,
An external gear and an internal gear rotatably engaged to adjust the inclination of the seat back relative to the seat base;
A bearing disposed so that an outer surface thereof contacts an inner ring of an axial hub formed by the internal gear;
An eccentric carrier configured to press a pair of wedges radially outward against the inner surface of the bearing;
A rotation adjusting element for providing a rotational drive to the eccentric carrier;
Including
The eccentric carrier is
A circumferential portion disposed around an axis and including an inner peripheral surface and an outer peripheral surface;
A carrier tab extending radially from the outer peripheral surface and disposed between the pair of wedges ;
And a drive tab extending outwardly along said axis from spaced and the circumferential portion from said shaft,
The rotation adjusting element includes a track support disposed between the inner surface of the bearing and the outer peripheral surface of the eccentric carrier to prevent the pair of wedges from being displaced from the wedge load surface region of the outer peripheral surface of the eccentric carrier. Including the body,
The carrier tab includes a carrier tab load surface proximate to an inner surface of the bearing surrounding the eccentric carrier;
A reclining mechanism in which the inner peripheral surface is approximately circular but not circular. The eccentric carrier is rotated by engagement with the drive tabs and the rotating adjustment element, the reclining mechanism according to claim 1. A major portion of the inner peripheral surface extends about the axis from the axis by a first distance;
The inner circumferential surface includes at least one contoured portion;
The reclining mechanism according to claim 1, wherein a radial distance from the axis along the contoured portion is larger than the first distance. The external gear has a center hub that defines an axial opening on the radially inner side of the eccentric carrier,
The inner peripheral surface, the first contoured portion of including having an arc shape extending in the circumferential direction in the radially inward of the carrier tab, reclining mechanism according to claim 1. The inner peripheral surface, a second contoured portions including facing the first contoured portion along said inner peripheral surface, the reclining mechanism according to claim 4. The first contoured portion includes two opposing ends ;
Oite the inner peripheral surface to the two opposite ends, changes from state away greater than a predetermined distance from said axis to said predetermined distance equal state from the axis, the reclining mechanism according to claim 4 . The outer peripheral surface is interrupted by the carrier tab;
The external gear comprises an outer portion, an intermediate portion of the teeth on the radially inner side of the outer portion, and an external gear having an inner portion in the radial direction inner side of the intermediate portion,
Each of the wedges includes an outer surface that engages with the inner surface of the bearing, and an inner surface that engages with the outer peripheral surface of the eccentric carrier,
It said intermediate portion the internal gear and engaging said inner portion has the cell Ntahabu, recliner mechanism of Claim 4. The inner circumferential surface includes a first contoured portion radially inward of the carrier tab;
The reclining mechanism according to claim 7 , wherein the eccentric carrier does not engage with the center hub at the first contoured portion. The reclining mechanism according to claim 8 , wherein the inner peripheral surface includes an inner load region that is disposed on both sides of the carrier tab and receives a load from the center hub , corresponding to the pair of wedges. The inner circumferential surface includes a second contoured portion disposed on the radially opposite side of the carrier tab along the inner circumferential surface,
The reclining mechanism according to claim 8 , wherein the second contoured portion does not engage with the center hub.

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